Change giving vending machine



June 1942- r K. H. LUNIDQVIST ETAL 2,238,249

CHANGE GIVING VENDING MACHINE Filed April 3, 1940 I 4 Shee ts-Sheet 1 0 l0 42 i i 5 3,4 i v 200 gil 4Q ,1 mm. 06.9.

KWWWL' mu A 'Y- June 1942- K. H. LUNDQVIST arm. 2,238,249

CHANGE GIVINGVENDING MACHINE Filed April 3, 1940 4 Sheets-Sheet 2 \NVENTOrQS e4 ML W ATT'Y.

June 30, 1942. K. H. YLUNDQVIST. ETAL CHANGE GIVING VENDING MACHINE Filed April 3, 1940 4 Shets-Sheet 5 W A Y.

June 30, 1942. K. H. LUNDQVIST ETAL CHANGE GIVING VENDING MACHINE 4 Sheets-Sheet 4 Filed April 3, 1940 Karl Lund V IH' Karl Ma-Hs vn' 01 YN ETO m ATT Y.

Patented June 30, 1942 2,288,249 CHANGE GIVING VENDING MACHINE Karl Hilding Lundqvist, s. Hammarbyhojden, Stockholm, and Karl Matts Vigborg, Stockholm,

Sweden, assignors to Kooperativa Forbundet Forening U. P. A., Stockholm, Sweden Application April 3, 1940, Serial No. 327,606 In Sweden February 6, 1939 6 Claims. (01. 194-75) The present invention relates to coin controlled machines, and, more particularly, to change giving vending machines, in which a number of change delivery devices is controlled by corresponding change delivery discs geared to a resilient drive member and to a summator which, upon the insertion of coins into the machine, releases said delivery discs for rotation through an angle proportional to the total value of the inserted coins.

One object of the invention is to provide a relatively simple mechanism for restoring the delivery discs of a machine of this type to their normal or rest positions.

Another object of the invention is to produce a restoring mechanism for the delivery discs which completes the restoring operation at a high speed.

A special object of the invention is to provide a fast operating cam restoring mechanism for a machine of the type described and claimed in our copending application, Ser. No. 303,212 in which the various delivery discs are carried on partly on a main delivery shaft and partly on an auxiliary delivery shaft with suitably proportioned reducing gearing between said shafts.

Still another object of the invention is to design a change giving vending machine, in which the change delivery discs are so rapidly restored to their rest positions that the machine, immediately after completion of one operation, is ready for a subsequent operation.

These and other objects are accomplished, according to the invention, by the arrangement and combination of elements set forth in the following detailed description, defined in the appended claims and illustratively exemplified in the accompanying drawings in which:

Figure l is a plan view of a change giving vending machine, the members for entering, the coins in and delivering the same from the machine being omitted for the sake of greater clarity.

Figure 2 is a section taken on the line II--II in Figure 1.

Figure 3 is an elevational view of a detail as indicated by the line III-III in Figure 1.

Figures 4-9 show a series of delivery discs suitable for a slightly modified machine, said discs being seen in the direction of the arrow in Fig. 1.

Figure shows on a larger scale a section taken on the line X--X in Figure 1.

Figure 11 is a plan view of Figure 10. Figure 12 shows on a larger scale a detail of the summator, the same being viewed along the section line XIIXII in Figure 13, which latter is a plan view of the said detail.

Figures 14 and 15 show on a larger scale the coupling between a toothed wheel of the driving mechanism of the machine and the summator in two elevations at right angles to each other.

Figure 16 shows a part of a coin delivery device in elevation.

Figure 17 shows, partly in section and partly in elevation, a coin operating impulse mechanism. I

Figure 18 is a plan view of the same mechanism with the uppermost portion of Figure 17 cut away and certain parts omitted.

Figure 19 is an elevational view of the means for ejecting change coins from the machine,

' Figure 20 is a vertical section through a coupling device for the operating shaft.

Figure 21 is an elevational view, on a larger scale, of a movable stop element and of the cam controlling the same.

Figure 22 is a top plan view, on a larger scale, of the main driving pinion and the adjacent end of the drive spring.

Figures 23 and 24 are elevational views, on a larger scale, of the gear release means and of the restoring means, respectively, for the auxiliary delivery shaft.

The change giving vending machine, according to the present invention, comprises a summator, i. e. a coin controlled mechanism including a rotary part which is normally held against rotation, and which, upon the insertion of coins into the machine, is released to permit a rotary adjustment of said member through ,an angle pro- .portional to the total value of the inserted coins.

A summator of this type is shown and described for instance in U. S. Patent 2,173,264.

In the present embodiment, however, the design of the members of the summator and its mode of operation differ somewhat from those of the patent. As shown, a number of sleeveshaped elements I are'mounted on a shaft 4 supported in a frame 3. All the elements I are rotatable about shaft 4 with the exception of the last element l on the right hand side of the machine which is fixed to the frame 3 by means of a pin 2. Discs I04, having each a hub portion 2|,

are axially displaceably and rotatably carried on the shaft 4 alternately with the elements I. Pins 20, which arefixed in the hub IQ of a toothed disc ll, project in axial direction into suitable bores provided in the hub portion N of the first disc I04 on the left hand side of the machine. Similar pins 20 couple the first element I on the left the highest denomination is 200 and the lowest denomination is 5, the disc I04 corresponding to the lowest denomination will thus have 40 teeth, The disc I04 corresponding to the value 10, said disc having consequently 20 teeth, is shown in Figures 12 and 13. The embodiment of the apparatus now described is adapted for Swedish currency. The mechanism is likewise adaptable for other monetary systems after slight alterations apparent to those skilled in the art.

Impulse members 6 actuatable by coins entered in the machine are capable of imparting a reciprocating motion to the discs I04, as will be described in more detail later on in connection with Figures 17 and 18. Owing to this reciprocation, the discs I04 are released for rotation and turned substantially in the manner disclosed in detail in the U. S. Patent No. 2,173,264. In the present case, however, the locking member for each disc I04 comprises two teeth IOI, I02 which are fixed to or formed from an arm I03 projecting radially from the adjacent sleeve member I. The teeth IOI, I02 are axially and angularly offset with respect to each other, see Figures 12 and 13. The spring force acting on the discs I04 is obtained by means of a helical spring I wound around a shaft 8, one end of said spring being at I05 fixed to said shaft 8 rotatably mounted in the frame 3 (see Fig. 1), the other end of the spring at 9 (Figures 2 and 22) being united with a main driving pinion II rotatable on the shaft 8. The spring tension is obtained by means of an arrangement described hereinafter more in detail.

The pinion I I meshes with a toothed wheel I3 on the shaft I2 (Figure 2), said wheel I3 in its turn meshing with a smaller toothed wheel I4 rotatable on the shaft 4. With the toothed wheel I4 is rigidly united a larger toothed wheel I5, provided with two axially projecting pins I6, adapted to be inserted into two of forty apertures I8 in the disc I! (Figures 14 and 15), which latter together with its hub I9 is rotatably and axially displaceably mounted on the shaft 4. When the pins I3 project into the apertures I8 in the manner shown in Figures 1 and 15, the spring I through the medium of the toothed wheels II, I3, I4 and I5 will strive to rotate the disc IT in the direction indicated by an arrow in Figure 2. However, the pins couple the hub I9 of disc I1 and the sleeve members I (except the last one on the right hand end of the machine) constantly to the hubs 2I of the next succeeding discs I04, respectively (counted from left to right in Figure 1), and as long, as no coin is inserted, each sleeve element I is locked to the preceding disc I04 by tooth IOI on arm I03 engaging a tooth of said preceding disc I04. Since the last member I at the right hand end of the machine is held against rotation by means of the pin 2, the spring 'I is prevented from rotating the disc IT, as long as no coin is inserted into the machine. When, however, one or several coins are inserted into the machine, the impulse members 6, by axially reciprocating the corresponding discs I04, will free each reciprocated disc. for a predetermined rotation. Upon movement in one axial direction, each disc I04 corresponding to an inserted coin is released from the arresting tooth IOI, whereby the released disc I 04, all the members I and hubs 2| between said disc and the spring driven disc I! and said disc I'I itself are permitted to rotate until the released tooth on the disc I04 strikes against the tooth I02 on arm I03, When the disc I04 then returns to its original axial position, it is freed from tooth I02, and a further rotation of the reciprocated disc I04, intermediate members I and 2I and toothed disc II takes place, until the next tooth on the released disc I04 engages tooth IOI. If the disc I04, corresponding to a coin value 200, which disc has only a single tooth, is actuated, the disc I! will be permitted to carry out a full rotation; if the disc I04 corresponding to a coin value 5 and having 40 teeth is actuated, the disc I! will rotate through an angle of 9. If both said discs I04 are actuated simultaneously, the total rotation of wheel II will be 369. Thus, the total angle of rotation of disc I"! and wheel I5 coupled thereto will always be proportional to the total value of the coins entered into the machine, between the portions of the summator, as set forth in the U. S. Patent No. 2,173,264. The disc II has on its periphery teeth with which a spring actuated detent I0 cooperates.

The toothed wheel I5 meshes with a toothed wheel 23 secured to the rotatable main delivery shaft 22 of the machine, the delivery discs 5, I0, 25, 50 on the said shaft controlling the delivery of 5, 10, 25 and 50 fire pieces, respectively, will, therefore, be turned by the spring I through an angle corresponding to the entered amount, when the pins I3 are inserted into the apertures I8 in the disc II. In the embodiment shown in Figures l and 2, the gear wheel 23 of the main delivery shaft 22 is geared to the toothed wheel I5 at the ratio 2 to 1 and capable of assuming 20 different angle positions for each rotation of the toothed wheel I5 through 180.

The discs I00, 200, controlling the delivery of 1 krona and 2 kronor pieces, respectively, are secured to a separate auxiliary delivery shaft 26, disposed coaxially with the main delivery shaft 22. The disc I00 is rigidly united with a toothed wheel 21 which meshes with a toothed wheel 29 mounted rotatably on one end of a shaft 28 being in turn rotatable in a frame portion. To the shaft 20 are secured, adjacent the toothed wheel 29, a toothed wheel 30 of the same shape and size as the toothed wheel 29, and, on the opposite end of shaft 28, a toothed wheel 3I which is adapted to cooperate with a disc 33 having, in the embodiment of the invention illustrated in Figures 1, 2, 9 and 10, a single tooth space 32, said disc 33 being fast on the shaft 22 (Figures 10, 11). A coupling wheel 36 carried by an arm 35 rockable about a shaft 34 is adapted to be brought into and out of driving mesh with the toothed wheels 29, 39. If the wheel 36 meshes with the toothed wheels 29, 30, the disc 33, upon each full rotation of the shaft 22, will impart a turning movement to the wheel 3I, said movement being transmitted via the wheels 30, 35 and 29 to the toothed wheel 21. The discs I00 and 200 will thus also assume an angle position corresponding to the entered amount.

The cam discs 5, I0, 25, 50, I00 and 200, shown in Figures 4 to 9, are designed for a slightly modified embodiment of the invention, in which the gear wheel 23 is geared to the toothed wheel I5 at the ratio 1 to 1 so that the shaft 22 is capable of assuming 40 angle positions corresponding to the 40 angle positions of the discs I04. The gear disc 33 is, in this case, provided with two diametrically opposed tooth spaces 32, so that the auxiliary shaft 26 will be turned one step, each time the shaft 22 has completed half a revolution. In Figures 4 to 9, the delivery dies 5, I0, 25, 50, I and 200 are shown in their nochange positions, which they assume if the sum of the inserted coins corresponds exactly to the price of the article sold by the machine. It will be understood that the shaft 22, and, if the price of the article exceeds 1 krona, also the auxiliary shaft 26, must be adjusted to normal or rest positions in which the delivery discs are angularly displaced from their no-change positions in the direction opposite to that indicated by the arrows in Figures 4 to 9 to an extent determined by the price of the article sold by the machine. This adjustment is effected as follows: While maintaining the driving connection between shafts 22 and 26, shafts 22 and 26 are put out of driving connection with the toothed wheel I5 and the segment gear 51, respectively. The shaft 22 is then turned in clockwise direction (as seen in Figures 4 to 9 through an angle corresponding to the determined price of the article. Thus, if the determined selling price is 50 Swedish ore, the shaft 22 is turned, in the embodiment shown in Figures 4 to 9, through an angle of 90; if the price is 1 Swedish krona, the shaft 22 is turned through 180 and the auxiliary shaft 26 with the disc I00 and 200 is turned one step in clockwise direction (as seen in Figures 4 to 9). After the adjustment of shafts 22 and 26, the shafts are again drivingly connected with the toothed wheel I5, and the gear 51, respectively, the cam disc 49, described in more detail later on, is reset on shaft 22 to the position shown in Figures 2 and 21, and the machine is ready for operation.

If the selling price of the article is, for instance, 25 ore, the shaft 22 has been adjusted to a position in which the discs 5, I0, 25 and 50 are displaced 45 in clockwise direction (as seen in Figures 4 to 9) from their no-change positions. Assuming, now, that coins to the value of 50 ore are inserted into the machine, the summator will release the delivery shaft 22 for a clockwise rotation through 90, and this shaft with the discs 5, I0, 25 and 50 will thus be brought into a position in which 25 (ire change are delivered, as will be described later on.

The spring 1, is maintained permanently at a predetermined tension by means of the device described hereinafter.

On the shaft 8 is fixed a disc 38 having recesses 31. A toothed wheel 39 is disposed rotatably and axially displaceably on the shaft 8 adjacent the disc 38, said wheel 39 being provided with projections 40 corresponding to the recesses 31. In driving mesh with the toothed wheel 39 is a toothed wheel I06, which is driven by a motor M. An adjustable helical spring 4I urges the wheel 39 against the disc 38 and strives to move the projections 40 into the recesses 31. The projections 40 will thus serve as driving members for the disc 38. After the projections 40 have rotated the disc 30 a certain number of revolutions and the spring 1 has received the desired tension, the spring M will allow the projections 40 owing to the resistance of the spring 1 to leave their engagement with the recesses 31. As soon as the tension of the spring 1 is lowered, the spring having been allowed to rotate the pinion II, the spring 4I presses once more the projections 40 into the. recesses 31. The tension of the spring 1 is thus held substantially constant.

The discs 5, I0, 25, 50, I00 and 200 are restored to their normal or rest positions at a predetermined stage of each operation of the machine by means of the following arrangement:

A shaft 42, which at a predetermined moment can be rotated 360 by means of a coupling 335 on the shaft 42, said coupling being described more in detail hereinafter, has secured thereto two cam discs 43 and 44. A follower 45, provided on a spring actuated arm 46 rockable about the shaft 4, is held pressed against the cam disc 43, and, upon rotation of the latter, the end 41 of the arm is displaced, from its normal position (shown in full lines in Figure 21), to a position, shown in dot and dash lines, in Figure 21, in which it is disposed in the path of a projection 48 of a disc 49 secured to the shaft 22 by means of a set screw 4%. In its normal position, the end 41 of arm 46 permits said disc 49 to rotate in the direction indicated by an arrow in Figure 2. Against the cam face I01 of the cam disc 44 (Figure 3), there bears through spring action a pin 53 secured on an arm 52 rockable about a pivot 5I. Upon the rotation of the cam disc 44 the arm 52 will perform a rocking motion to and fro, and, by means of a fork member 55 united with the arm 52 and engaging a groove 54 in the hub portion I9 of the disc I1, the latter will be reciprocated on the shaft 4, and the apertures I8 of said disc will consequently engage and disengage the pins I6 on the toothed wheel I 5. I

Further cam discs BI and 65 on shaft 42 actuate, during rotation of the latter shaft, Y- shaped arms 63 and 66, respectively, said arms being rockable about a shaft 62. The arm 63 is connected through a link 64 with the arm 35 carrying the coupling wheel 36, while arm 65 is connected with a link member 59. A gear segment 51 rockable about a shaft 56 and meshing with the toothed wheel 21 carries on a lever arm extending beyond its pivot axis a pin 60 guided in a longitudinal slot 58 of link 59. Elements 6!, 65, 63, 66, 64, 59, 51, and 60 serve to restore the auxiliary delivery shaft 26 to its rest position, as will be described later on.

The abovementioned coupling 335 for restricting the rotation of the shaft 42 to one revolution is substantially constructed as the corresponding coupling in the British Patent No. 440,763, but owing to a slight alteration the coupling is described hereinafter with reference to Figures 1 and 20.

A coupling box 338 is fixed to the shaft 42. Into said box there extends a bushing or sleeve 336, having fixed thereto a toothed wheel 34I, which is in driving mesh with the toothed wheel 39, and a cam member 342. An inwardly projecting tooth 345 on a displaceable ring 346, disposed radially displaceably in said box 338 for rotation therewith, is adapted to be engaged by the teeth 343 of said cam member, when the ring 346 is shifted to its one radial end position in the manner set forth in the British Patent No. 440,763. After a rotation through 360 the projection 348 of the ring 346 through cooperation with the stationary pin 350 shifts the ring 346 back to its inoperative position, thus ensuring that only one full rotation of the shaft 42 is effected.

The coins are entered into the machine via coin chutes I08 (Figures 2, 1'1 and 18), the number of which in the present case corresponds to the number of discs I04 and discs 5, I0, 25, 50, I and 205 respectively. The coins, in passing the coin chutes I08, cooperate with the correspond ing impulse members 6, as will be described hereinafter in connection with Figures 17 and 18. Each coin chute I08 is connected to a coin receptacle I39. Each coin ejection device comprises an ejecting member III adapted to be reciprocated by a gear segment I I0 and an arm I I3 adapted to be rocked upwards and downwards by a cam disc I I2 on shaft 42, said disc I I 2 being so shaped that the arm H3 and the plunger II4 are retained in the position shown in full lines in Figure 16 until the counting process has been finished and the delivery discs 5, I0, 25, 50, I03 and 290 of the machine have assumed their positions corresponding to the entered amount, said plunger H4 forming the bottom of the coin receptacle. The counting process having been finished and rotation of shaft 42 having been started, the arm II3 performs a rocking movement. The pin II5 on the underside of the plunger H4 is then allowed to move down and, according to the angular position of the corresponding delivery disc, to bear against the periphery of said disc or to enter someone of the recesses provided in the disc as shown in dotdashed lines in Figure 16. If a pin H5 bears against the periphery of the corresponding delivery disc, the ejecting member I I I, being displaced and passing through apertures in the wall of the coin receptacle and through a groove H6 in the plunger II4 (see Fig. 1'7), will not strike or take along any coin, but, if a pin Il5' enters one of the recesses in the corresponding delivery discs, the front end of the ejecting member strikes and pushes out one or more coins through the slot H1 in the receptacle, the depth of the recess entered by the pin I I5 determining the number of coins ejected. The ejected coins fall through a coin chute I29 to the delivery opening of the machine.

How the segment gears H0 are rocked to and fro will be seen most clearly from Figure 19. This figure shows that the segments IIO are fixed to a shaft II8 visible also in Figure 2. At one end of said shaft II8 there is fixed an arm H0 which by means of a link member I20 is united with a pin I22 eccentrically located on a disc I2l. The rotation of the disc I2,I fixed to the shaft 42 will thus rock the shaft H8 to and fro, and the segment gears through their cooperation with the teeth I23 of the members I II will cause the latter to perform a rectilinear reciprocating motion in their guides I24 (Figure 2).

Above each coin receptacle I09 there is inserted in the coin chute I08 a plunger I26 having a central boring I25, Figures 17 and 18. One end of a hook-shaped member I21 fixed to the corresponding impulse member 6 bears against the plunger I26 and through the action of a draw spring I28 united with the member 6, which member is rockable about a pin I33, the member I21 strives to press the plunger into the position shown in full lines in Figures 17 and 18. At each coin chute I08 there is also a cross piece I 3| interposed between two displaceable rods I30, said cross piece having fixed thereto a pin I32 of a smaller diameter than the boring I25 of the corresponding plunger I25, said pin I32 extending through an opening in the wall of the coin chute I08 to have its inner end face normally flush with the inner surface of said wall. Furthermore, there is provided an angle lever I351 rockable around a pin I34, said lever being actuated by a spring I36 (Figure 17). .One end of said lever is intended for cooperation with a notch I31 in the member 0 as will be described hereinafter more in detail.

When a coin I38 is inserted in a coin chute I08 the coin will remain in the position shown in Figure 1'7, the chute portion beneath the plunger I26 being laterally offset relative to the upper chute portion (see Fig. 17). If the rods I30,

for'instance by depression of an operating mem-' ber accessible from the outside of the machine, are displaced in the direction indicated by an arrow in Figure 18, the inserted coin will prevent the pin I32 from entering the boring I25 in the plunger I26. The latter will instead be forced against the action of the spring I28 into the position indicated by dot-dashed lines in Figure 1'1. The member 6 is simultaneously caused to perform a rocking movement, one end of the arm I35 being thereby brought to engage the notch I31, and the corresponding disc !04 is axially displaced by the lower forked portion I39 of the member 6. The coin has simultaneously been brought into register with the offset downward continuation of the coin chute I08. If the rods Is30 are now allowed to return to their initial position, the member 6 will for a short time be retained in its displaced position owing to the cooperation between the arm I35 and the notch I31. Therefore, when the pressure of the pin I32 against the coin ceases the coin is freed to fall down into the coin receptacle I09. Immediately before reaching its initial position the cross piece I3I brings the arm I35 out of engagement with the notch I31, the member 6 being thereby rocked back to its initial position by the spring I28. During the to and fro rocking motion performed by the member 6, the corresponding disc I04 is first released from tooth IOI and, thereafter, from tooth I82 of the corresponding locking member IE3 and is thus allowed to rotate through an angle in proportion to the entered coin denomination. The action of the spring 1 is transmitted to the released discs I04 through the toothed wheels II, I3, I4 and I5, the pins I6, the toothed wheel I1 and the pins 20 coupling the hub portion I9 of the wheel I1 and the sleeve elements I to the hubs 2I of the discs I04. The discs I34 in the corresponding coin chutes I68 of which no coin has been entered have not been reciprocated, since the corresponding pins I32 have passed into the borings I25 of the plungers I26. Said plungers and the members 6 cooperating therewith have thus remained in their positions, and the corresponding discs I04 have remained locked to the succeeding sleeve members I by their locking members I03.

A short summary of the entire counting process will be given hereinafter.

Coins amounting to a value equal to or more than the price of the article or the ticket are entered through the coin slots of the machine. By means of electrical contact devices in the coin chutes the electrical motor driving the toothed wheel I06 is put into function immediately after entering the first coin. During the entering of the coins the toothed wheel 39 and the disc 38 are thus rotated, i. e. the spring 1 is wound. When the required number of coins has been entered the rods I30 are displaced in the manner described above, and those discs I04, into the corresponding coin chutes of which coins have been entered, are displaced axially and turned,

relative to the next succeeding sleeve members I, through an angle in proportion to the denomination of the entered coin. The disc I1 and toothed Wheel I5, thus, rotate through a total angle proportional to the total value of all the coins entered into the machine. Shaft 22 is rotated by gear 23 in mesh with toothed wheel I5, and this rotation of shaft 22 is transferred to the shaft 26 by means of the gearing 33, 3|, 36, 36, 29 and 21 described before in detail. During said transfer the segment gear 51 rockable about a shaft 56 and meshing with the toothed Wheel 21 is rocked in the direction indicated by an arrow in Figure 2, and the pin 56 guided in the slot 58 of the link member 56 performs a movement corresponding to the movement of the segment gear 51.

After the counting process has been completed another operating member accessible from the outside is depressed, putting the coupling 335 into function via a pin 334. This may, of course, be effected in the manner set forth in the British Patent No. 440,763. This coupling having been put into function, the shaft 42 starts rotating and causes delivery of the article by any known means, as for instance those described in the British patent 440,763. Simultaneously, the arms II3 perform their rocking movements and, immediately thereafter, the ejecting members I I I are displaced towards the right (in Figure 2). After the article and also the balance, if any, have been delivered, the arms I I3 and the members III return to their initial positions.

The discs 5, I0, 25, 50, I60 and 200 are returned to their rest positions in the following manner: First, during the displacement of the ejector members III towards the right, the cam disc 43 rotating with the shaft 42 causes the end 4! of the arm 46 to assume a position in the path of projection 48 on disc 49, as indicated in dot and dash lines in Figures 2 and 21. Next, cam discs 6| on the shaft 42 operate the Y-shaped arm 63 and the link-member 64 to rock the arm 35 in the direction indicated by the arrow in Figure 23, thereby causing the coupling wheel 36 to leave its engagement with the toothed wheels 29 and 3|]. Simultaneously, the arm 52, through the action of cam face III'I of cam 44 on the pin 53, displaces the forked portion 55 and the disc I I in such a manner that the pins I6 cease to cooperate with the apertures I8 of the disc I1, which latter has been arrested by the summator in the angular position assumed at the end of the counting operation. As a result, the gears I I, I3, I4 and I are freed to transmit the turning force of the spring I once more to the toothed wheel 23 on the shaft 22. At this moment, the shaft 22 is still locked against rotation by the pins H5 being in engagement with the recesses of the corresponding delivery discs, but, when, upon continued rotation of shaft 42, the cam [I2 rocks the arm II3 to lift the plungers H4 and pins II5, the shaft 22 is rotated in clockwise direction (as seen in Figure until the projection 48 of the disc 49 strikes against the end 41 of arm 46, whereupon the shaft 22 stops with the discs 5, I0, 25 and 5!] assuming their normal or rest positions. Immediately after the upward displacement of pins II5, the cam discs 65 displace, through the Y-shaped arm 66, the link member 59 in the direction indicated by the arrows in Figures 2 and 24, and, when the right hand end of the slot 58 strikes against the pin 60, the segment gear 51 is rocked in a clockwise direction (as seen in Figures 2 and 24) through an angle equal to that of the counterclockwise movement carried out by the segment gear 51 during the preceding counting operation. In this manner, the toothed wheel 21 and the auxiliary shaft 26 with the discs I00, 200 are restored to their rest positions in a counterclockwise movement.

Towards the end of the rotation of shaft 42 through 360, the cam 44 permits the fork 55 to return the disc 11 into engagement with the toothed wheel I5, whereupon the arm 46 is forced by the cam disc 43 to assume its inactive lower position. The shaft 22 is then retained in its angular rest position by the engagement between toothed wheel I5 and disc I1 and no longer by the end 4'! of arm 46. Approximately simultaneously with the downward movement of the arm 66, the cam 55 returns the striker member 59 to its right hand position without causing any movement of segment gear 51. Finally, the coupling wheel 36, having been retained in its angle position by a spring actuated locking roller 61, is returned into engagement with the wheels 29 and 36 by the link 64, arm 63 and cam disc 6I.

When the shaft 42 has completed a full rotation, the oblique surface of the projection 348 cooperates with the stationary pin 350 and returns the ring 346 to its initial position where upon the shaft 42 stops turning. Simultaneously, the current to the electrical motor is automatically broken. The machine is thus ready for a new operation.

As will be clear from the foregoing description, the discs 5, I6, 25, and 50 are rotated in the same (clockwise) direction during the restoring operation and during the counting operation, while the discs I60, 260, during the restoring operation, are rotated in a (counterclockwise) direction opposite to their direction of rotation during the counting operation.

Having now described our invention, what We claim as new and desire to secure by Letters Patent is:

1. In a machine of the type described having a rotary member, means to give to said rotary member a tendency for rotation in a predetermined direction, and a coin controlled summator including a rotary part normally coupled to said rotary member, said rotary part being normally held against rotation and being released upon the application to said summator of selected impulses, each representing a predetermined value, to permit a rotary adjustment of said rotary member through an angle proportional to the total value of the applied impulses, the combination of a mechanism for restoring said rotary member to a predetermined angular rest position, said restoring mechanism comprising a stop element adapted to assume alternatively a normal inoperative position and an operative poition in which it arrests said rotary member whenever the latter, during its rotation in said predetermined direction,-reaches said predetermined rest position, means, operative after each impulse-controlled adjustment of said rotary member to uncouple the latter for a predetermined length of time from said rotary part so as to permit further rotation of said rotary member in said predetermined direction, and control means for said stop element to shift the same at a certain early stage of each restoring operation to said operative position and to return said step element to its inoperative position after the cou pling between said rotary part and said rotary member has been restored.

2. A machine, as claimed in claim 1, in which said cam restoring mechanism includes an operating shaft and means to rotate said operating shaft, for each restoring operation, through a predetermined angle, said uncoupling means and said stop control means each including a cam mounted on said operating shaft.

3. In a change giving vending machine having a rotary drive member, means to give to said drive member a tendency for rotation in one direction, a coin controlled summator including a rotary part normally coupled to said drive member, said rotary part being normally held against rotation and being released, upon the insertion of coins into the machine to permit a rotary adjustment of said drive members through an angle proportional to the total value of the inserted coins, a series of change delivery devices adapted to effect the delivery of coins of different denominations, respectively, and a series of change delivery discs controlling the different change delivery devices respectively, the combination of a main delivery shaft, means drivingly connecting said drive member with said main delivery shaft to give the latter a tendency for rotation in a predetermined direction, said main delivery shaft having secured thereto some of said change delivery discs, respectively, controlling change delivery devices for coins of lower denominations, an auxiliary delivery shaft, having fixed thereto at least one of said change delivery discs controlling a change delivery device for coins of a higher denomination, releasable gearing between said main and auxiliary delivery shafts, said gearing being adapted upon a coin controlled rotary adjustment of said main delivery shaft through a predetermined angle to effect a coin controlled rotary adjustment of said auxiliary delivery shaft through a predetermined smaller angle, and a mechanism for restoring said delivery shafts to predetermined anguler rest positions, said restoring mechanism comprising a stop element adapted to assume alternatively a normal inoperative position and an operative position in which it arrests said main delivery shaft Whenever the latter, during its rotation in said predetermined direction, reaches its predetermined angular rest position, means, operative after each coin controlled adjustment of said delivery shafts, to uncouple said rotary part 1 for a predetermined length of time from said drive member so as to permit further rotation of said main delivery shaft in said predetermined direction, control means for said stop element to shift the same, at a certain early stage of each restoring operation, to said operative position and to return it to its inoperative position after the coupling between said rotary part and said drive member has been restored, means to release the gearing between said delivery shafts approximately simultaneously with the uncoupling of said rotary part from said drive member and to reestablish said gearing after a predetermined time interval, and means operative between the release and the reestablishment of said gearing to turn said auxiliary delivery shaft in opposite direction through the angle through which it has been rotated during its preceding coin controlled adjustment.

4. A machine as claimed in claim 3, in which said restoring mechanism includes an operating shaft and means to rotate said operating shaft, for each restoring operation through a predetermined angle, said uncoupling means, said stop control means and said gear releasing means, each including a cam mounted on said operating shaft.

5. A machine, as claimed in claim 3, in which said turning means for said auxiliary delivery shaft comprises a striker member, means to reciprocate said striker member from a first predetermined position to a second predetermined position and back to said first predetermined position, and an element permanently coupled to said auxiliary delivery shaft and having a portion projecting into the path of said striker member, said portion being displaced during the coin controlled adjustment of said auxiliary delivery shaft, along said path from a rest position adjacent said second predetermined position of said striker member towards said first predetermined position of the latter and being returned to its rest position when said striker member is reciprocated therebyrestoring said auxiliary delivery shaft to its rest position.

6. A machine, as claimed in claim 3, in which said restoring mechanism includes an operating shaft and means to rotate said operating shaft, for each restoring operation, through a predetermined angle, and said turning means for said auxiliary delivery shaft comprises a striker member, means to reciprocate said striker member from a first predetermined position to a second predetermined position and back to said first predetermined position, and an element pennanently coupled to said auxiliary deliver shaft and having a portion extending into the path of said striker member, said portion being displaced, during the coin controlled adjustment of said auxiliary delivery shaft, along said path from a rest position adjacent said second predetermined position of said striker member towards said first predetermined position of the latter and being returned to its rest position when said striker member is reciprocated, said uncoupling means, said stop control means, said gear re-- leasing means and said reciprocating means for said striker member, each including a cam mounted on said operating shaft.

KARL HILDING LUNDQVIST. KARL MATTS VIGBORG. 

